WO2018066223A1 - 遠心クラッチ - Google Patents

遠心クラッチ Download PDF

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Publication number
WO2018066223A1
WO2018066223A1 PCT/JP2017/028742 JP2017028742W WO2018066223A1 WO 2018066223 A1 WO2018066223 A1 WO 2018066223A1 JP 2017028742 W JP2017028742 W JP 2017028742W WO 2018066223 A1 WO2018066223 A1 WO 2018066223A1
Authority
WO
WIPO (PCT)
Prior art keywords
clutch
drive plate
centrifugal
torsion spring
weight
Prior art date
Application number
PCT/JP2017/028742
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
友太 横道
薫 青野
Original Assignee
株式会社エフ・シー・シー
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社エフ・シー・シー filed Critical 株式会社エフ・シー・シー
Priority to CN201780057181.3A priority Critical patent/CN109844345B/zh
Priority to EP17858063.5A priority patent/EP3524842A4/en
Priority to US16/339,660 priority patent/US11060569B2/en
Publication of WO2018066223A1 publication Critical patent/WO2018066223A1/ja

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D43/18—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members with friction clutching members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D2043/145—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members the centrifugal masses being pivoting
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2300/00—Special features for couplings or clutches
    • F16D2300/22—Vibration damping

Definitions

  • the present invention relates to a centrifugal clutch that blocks transmission of rotational driving force to the driven side until the engine reaches a predetermined rotational speed and transmits rotational driving force to the driven side when the engine reaches a predetermined rotational speed.
  • centrifugal clutches that transmit rotational driving force to the driven side when the engine reaches a predetermined rotational speed are used.
  • three clutch weights arranged to extend in a circumferential direction on an annular second drive plate in plan view are elastically connected to each other by a connection spring, and the outer side of the second drive plate.
  • positioned in is disclosed.
  • connection spring is connected to the substantially central portion of the clutch weight extending in the circumferential direction of the second drive plate, the displacement of the clutch weight in the centrifugal direction is restricted.
  • a connecting spring having a large elastic force (tensile force) is required, and it is difficult to secure a required clutch capacity (a magnitude of power transmitted by the clutch) and the apparatus configuration is enlarged.
  • the present invention has been made to address the above-described problems, and an object of the present invention is to provide a centrifugal clutch that can easily secure a clutch capacity without increasing the size of the apparatus.
  • the present invention is characterized in that a drive plate that rotates integrally with a driven pulley under the driving force of an engine, and a cylindrical surface provided concentrically with the drive plate on the outside of the drive plate.
  • the clutch outer has a clutch shoe that extends along the circumferential direction of the drive plate and faces the cylindrical surface of the clutch outer and is rotatably mounted on the drive plate via a swing support pin.
  • a plurality of clutch weights that swing in a direction to contact or separate from the cylindrical surface of the outer clutch according to the centrifugal force generated by the rotational drive of the plate, and a torsion spring that applies a force against the centrifugal force to the clutch weights
  • the torsion spring is a clutch that faces the cylindrical surface of the clutch outer. Of the two circumferential ends of the weight, it is disposed adjacent to the far end, which is the end far from the swinging support pin, and contacts the far end to exert a force against the centrifugal force. There is.
  • the centrifugal clutch has the torsion spring disposed adjacent to the far end of the clutch weight that swings with respect to the outer clutch, and one end of the torsion spring is Since the force is applied to the far end, which is the free end of the clutch weight, the displacement of the clutch weight in the centrifugal direction can be regulated with a force smaller than that of the prior art.
  • the centrifugal clutch according to the present invention it is possible to easily secure the clutch capacity without increasing the size of the apparatus.
  • the torsion spring is arranged at the outermost peripheral portion of the drive plate, the force that pushes the clutch weight radially inward by the centrifugal force generated by the rotational drive of the drive plate is reduced, and the clutch weight is moved to the clutch outer. It can be made easy to press.
  • the swing support pin is provided at a position adjacent to the far end of the clutch weight on the outer edge portion of the drive plate, and the torsion spring includes the swing support pin. It is to be supported by.
  • the centrifugal clutch has a swing support pin serving as a fulcrum for swinging the clutch weight at a position adjacent to the far end of the clutch weight on the outer edge of the drive plate. Since it is provided and supports the torsion spring, the components constituting the centrifugal clutch can be densified to reduce the device configuration.
  • the torsion spring is a spring support formed in a pin shape on the drive plate or the clutch weight in a state where the coil portion formed between both ends is unwound. It is that it is supported by being fitted to.
  • the centrifugal clutch is formed in a pin shape on the drive plate or the clutch weight with the coil portion formed between both ends of the torsion spring being rewound.
  • the clutch weight is displaced in the centrifugal direction by being fitted to and supported by the spring support, the inner diameter of the coil portion of the torsion spring is expanded and the frictional resistance between the spring support and the clutch weight is suppressed. It is possible to prevent an excessive force from acting on the torsion spring due to the displacement of.
  • the state in which the coil portion of the torsion spring is rewound means a state in which both end portions of the torsion spring are expanded in the direction of unwinding the coil portion.
  • the torsion spring is provided on the side opposite to the drive plate side in the clutch weight.
  • the centrifugal clutch has the torsion spring provided on the side opposite to the drive plate in the clutch weight, and therefore the torsion spring is interposed between the drive plate and the clutch weight.
  • the assembly work of the torsion spring can be facilitated, and the manufacturing burden and the maintenance burden can be reduced.
  • Another feature of the present invention is that, in the centrifugal clutch, one of both end portions of the torsion spring is engaged with the drive plate.
  • the centrifugal clutch has one end portion of the torsion spring that is engaged with the drive plate, so that the same end portion is engaged with the clutch weight. Compared to the case of this, the wear of the clutch weight and the torsion spring can be suppressed, and the torsion spring can be reduced in size to reduce the entire device configuration.
  • FIG. 2 is a partially broken plan view showing an internal configuration of the centrifugal clutch as viewed from line 2-2 shown in FIG. It is a perspective view which shows roughly the external appearance structure of the drive plate in the centrifugal clutch shown in FIG. 1 and FIG. 2, respectively.
  • FIG. 3 is a perspective view schematically showing an external configuration of a clutch weight in the centrifugal clutch shown in FIGS. 1 and 2 respectively.
  • FIG. 3 is a partially broken plan view showing a connected state in which a clutch shoe in the centrifugal clutch shown in FIG. 2 is in contact with an outer clutch.
  • FIG. 7 is a partially broken plan view showing the internal configuration of the centrifugal clutch as viewed from line 7-7 shown in FIG. It is a perspective view which shows roughly the external appearance structure of the centrifugal clutch shown in FIG. 6 and FIG. 7, respectively. It is a perspective view which shows roughly the external appearance structure of the drive plate in the centrifugal clutch shown in FIG. 6 and FIG. 7, respectively. It is a perspective view which shows roughly the external appearance structure of the centrifugal clutch which concerns on the other modification of this invention. It is a perspective view which shows roughly the external appearance structure of the clutch weight in the centrifugal clutch shown in FIG.
  • FIG. 1 is a plan sectional view schematically showing the configuration of a centrifugal clutch 100 according to the present invention.
  • FIG. 2 is a partially broken side view showing the internal configuration of the centrifugal clutch 100 as viewed from line 2-2 shown in FIG.
  • Centrifugal clutch 100 is a mechanical device that is provided between an engine and a rear wheel that is a driving wheel in a motorcycle such as a scooter to transmit or block the rotational driving force of the engine to the rear wheel.
  • the centrifugal clutch 100 is a mechanical device that transmits or interrupts the rotational driving force of an engine (not shown) to the drive shaft 101, and mainly includes a drive plate 110, four clutch weights 120, and a clutch outer 130.
  • the drive plate 110 is a component that is provided on the crankshaft 90 extending from the engine and is directly driven to rotate by the rotational driving force of the engine, and is configured by forming a metal material into a disk shape in plan view. More specifically, as shown in FIG. 3, the drive plate 110 has a fitting cylinder portion 112 in which the crankshaft 90 is spline-fitted at the central portion of the flat base 111. Further, the drive plate 110 is provided with four swing support pins 113, spring support members 115, and damper support pins 117 at equal intervals along the circumferential direction on the outer portion of the fitting cylinder portion 112 in the base 111. It has been.
  • the swing support pin 113 is a part for pivotally supporting one end side of a clutch weight 120 (to be described later) and swinging the other end side.
  • the swing support pin 113 is formed of a metal material in a pin shape. It is configured.
  • the swing support pin 113 is fixedly attached in a state where the swing support pin 113 stands on the inner side of the spring support 115 on the base 111 by an attachment bolt 113a.
  • the swing support pin 113 has an E ring 113b attached to the tip via a side plate 114.
  • the side plate 114 is a part for holding the four clutch weights 120, and is configured by forming a metal material in a ring shape.
  • the spring support 115 is a part for supporting the torsion spring 116, and is composed of a metal stepped rod. In this case, the spring support 115 is formed such that the outer diameter of the portion of the torsion spring 116 fitted into the coil portion 116a is smaller than the inner diameter of the coil portion 116a.
  • the spring support 115 stands up at a position on the base 111 adjacent to the far end 121a which is one of the circumferential ends of the clutch weight 120 facing a cylindrical surface 131 of the clutch outer 130 which will be described later. It is fixedly attached by mounting bolts 115a.
  • the torsion spring 116 is a component for applying a force toward the inside of the drive plate 110 to the clutch weight 120, and is configured by winding spring steel in a coil shape.
  • the torsion spring 116 is supported on the outer edge portion of the drive plate 110 in a state where the coil portion 116 a is fitted to the spring support 115 that stands between the two clutch weights 120.
  • the torsion spring 116 has two end portions 116b and 116c projecting from both ends of the coil portion 116a, and the far end of one clutch weight 120 in the two clutch weights 120 located on both sides of the torsion spring 116, respectively. 121a and the other end 121b of the other clutch weight 120.
  • the torsion spring 116 is hung on each clutch weight 120 in a state where both end portions 116b and 116c are spread in the direction of unwinding the coil portion 116a. Therefore, the torsion spring 116 is fitted and supported by the spring support 115 with the coil portion 116a being rewound.
  • the damper support pin 117 is a part for supporting the damper 118, and is composed of a metal rod.
  • the damper support pins 117 are fixedly provided in a standing state in the vicinity of the spring support 115 on the base 111 of the drive plate 110.
  • the damper 118 is a component that guides a swinging motion that causes the other end portion of the clutch weight 120 to approach or separate from the clutch outer 130 and serves as a cushioning material during separation, and the rubber material is formed in a cylindrical shape. Configured.
  • the damper 118 is fixedly fitted on the outer peripheral surface of the damper support pin 117.
  • the four clutch weights 120 drive the rotational driving force from the engine by contacting or separating the clutch outer 130 via the clutch shoe 123 according to the rotational speed of the drive plate 110. It is a component for transmitting or blocking to the shaft 101, and is configured by forming a metal material (for example, zinc material) into a curved shape extending along the circumferential direction of the drive plate 110.
  • a metal material for example, zinc material
  • the clutch weight 120 is formed in a block shape curved along the cylindrical surface 131 that is the inner circumferential surface of the clutch outer 130, and is centrifugally moved when the clutch weight 120 is rotated together with the drive plate 110. It functions as a weight for generating force.
  • the clutch weight 120 has one end side in the circumferential direction of the drive plate 110 bent toward the inner side of the drive plate 110 via a proximal end 121b to form a pin fitting hole 122. It is rotatably supported by a swing support pin 113 through 122.
  • the near end 121b is an end portion closer to the swing support pin 113 among the circumferential ends of the clutch weight 120 facing the cylindrical surface 131 of the clutch outer 130, in other words, It is a portion between the end of the both ends close to the swing support pin 113 and the end of the clutch shoe 123.
  • the pin fitting hole 122 is a portion in which the swing support pin 113 in the drive plate 110 is rotatably fitted, and is configured by a through hole penetrating in the thickness direction of the clutch weight 120. Further, the proximal end 121 b of the clutch weight 120 is pushed toward the inner side of the drive plate 110 by one end 116 c of the torsion spring 116.
  • the damper 118 is slidably fitted to the far end 121a side, which is the end portion far from the swing support pin 113 on the opposite side to the near end 121b in the clutch weight 120, and The torsion spring 116 is pushed toward the inner side of the drive plate 110 by one end 116b.
  • the far end 121b is an end portion of the clutch weight 120 facing the cylindrical surface 131 of the clutch outer 130 that is far from the swinging support pin 113, in other words, It is a portion between the end of the both ends that is far from the swing support pin 113 and the end of the clutch shoe 123.
  • the clutch weight 120 is provided with a clutch shoe 123 on the outer peripheral surface facing the cylindrical surface 131 of the clutch outer 130.
  • the clutch shoe 123 is a component for increasing the frictional force with respect to the inner peripheral surface of the clutch outer 130, and is configured by forming a friction material in a plate shape extending in an arc shape.
  • FIG. 2 a part of one of the four clutch weights 120 is broken and shown for easy understanding of the configuration of the clutch weight 120.
  • the crankshaft 90, the E-ring 113b, and the side plate 114 are omitted.
  • the clutch outer 130 is a component that is rotationally driven integrally with the drive shaft 101, and is configured by forming a metal material from the drive plate 110 into a cup shape that covers the outer peripheral surface of the clutch weight 120. That is, the clutch outer 130 has a cylindrical surface 131 that frictionally contacts the clutch shoe 123 of the clutch weight 120 displaced toward the outer periphery of the drive plate 110.
  • the centrifugal clutch 100 functions as a part of a power transmission mechanism (not shown) disposed between an engine and a rear wheel serving as a drive wheel in a motorcycle vehicle (for example, a scooter).
  • a power transmission mechanism not shown
  • the centrifugal clutch 100 blocks transmission of driving force between the engine and the drive shaft 101 as shown in FIG.
  • the drive plate 110 is rotationally driven by the rotational driving force of the engine transmitted through the crankshaft 90, and the clutch weight 120 is rotationally driven.
  • the centrifugal clutch 100 has a centrifugal force acting on the clutch weight 120 that is smaller than the elastic force (pressing force) of the torsion spring 116, so the clutch shoe 123 does not contact the cylindrical surface 131 of the clutch outer 130 and the engine. Is not transmitted to the drive shaft 101.
  • the torsion spring 116 is disposed in the vicinity of the far end 121a of the clutch weight 120 and presses the far end 121a, which is the free end of the clutch weight 120.
  • the displacement of 120 in the centrifugal direction can be regulated.
  • the centrifugal clutch 100 transmits the rotational driving force of the engine to the drive shaft 101 in accordance with an increase in the rotational speed of the engine due to the driver's accelerator operation in the motorcycle. Specifically, as shown in FIG. 5, in the centrifugal clutch 100, the centrifugal force acting on the clutch weight 120 becomes larger than the elastic force (pressing force) of the torsion spring 116 as the engine speed increases. The weight 120 is rotationally displaced outward in the radial direction around the swing support pin 113.
  • the centrifugal clutch 100 causes the clutch shoe 120 to rotate and displace toward the cylindrical surface 131 side of the clutch outer 130 while resisting the elastic force (pressing force) of the torsion spring 116 as the engine speed increases. 123 contacts the cylindrical surface 131.
  • the torsion spring 116 is opened when the four clutch weights 120 are rotated because both ends 116b and 116c are opened so that the coil 116a is rewound and the fitting state with the spring support 115 is more loosened. It becomes easier to rotate with respect to the support body 115.
  • the crankshaft 90, the E-ring 113b, and the side plate 114 are omitted.
  • the rotational drive directions of the drive plate 110 and the clutch outer 130 in the centrifugal clutch 100 are indicated by broken-line arrows, respectively.
  • the centrifugal clutch 100 maintains the state in which the clutch shoe 123 is pressed against the cylindrical surface 131 of the clutch outer 130, so that the drive plate 110 and the clutch outer 130 are rotated together to drive the drive shaft 101. Drive to rotate.
  • the motorcycle can travel by rotating and driving the rear wheels via a transmission (not shown) coupled to the drive shaft 101.
  • the centrifugal clutch 100 blocks transmission of the rotational driving force of the engine to the drive shaft 101. Specifically, in the centrifugal clutch 100, the centrifugal force acting on the clutch weight 120 becomes smaller than the elastic force (pressing force) of the torsion spring 116 as the engine speed decreases, so that the clutch weight 120 is swung. Rotate and displace inward in the radial direction centering on 113.
  • the centrifugal clutch 100 has the torsion spring 116 disposed adjacent to the far end 121a of the clutch weight 120 that swings with respect to the clutch outer 130, and Since one end 116b of the torsion spring 116 exerts a force on the far end 121a, which is the free end of the clutch weight 120, the displacement of the clutch weight 120 in the centrifugal direction is regulated with a force smaller than that of the prior art. be able to.
  • the centrifugal clutch 100 according to the present invention it is possible to easily secure the clutch capacity without increasing the size of the apparatus.
  • the torsion spring 116 is disposed at the outermost peripheral portion of the drive plate 110, the force that presses the clutch weight 120 radially inward due to the centrifugal force generated by the rotational drive of the drive plate 110 is reduced, and the clutch weight is reduced. 120 can be easily pressed against the clutch outer 130.
  • the torsion spring 116 is supported by a pin-shaped spring support 115 provided on the base 111 of the drive plate 110.
  • the spring support 115 is provided in a state where it stands between the two clutch weights 120 adjacent to each other at the outer edge portion on the base 111 of the drive plate 110.
  • the torsion spring 116 may be disposed at a position adjacent to the far end 121a in the clutch weight 120 facing the cylindrical surface 131 of the clutch outer 130. Therefore, the torsion spring 116 can be configured to be supported by the swing support pin 113 as shown in FIGS. 6 to 9, for example.
  • the swing support pin 113 can be disposed on the outer edge of the drive plate 110 at a position adjacent to the far end 121 a of the clutch weight 120.
  • three swing support pins 113 are provided to support the three clutch weights 120.
  • the clutch weight 120 is formed in a substantially arc shape extending along the circumferential direction of the drive plate 110 and extending to the swing support pin 113, and the spring support 115 and the pin fitting hole 122 are provided on the vicinity end 121b side, respectively. It is formed.
  • the spring support 115 is a portion into which the coil portion 116a of the torsion spring 116 is fitted, and is formed in a cylindrical shape in the thickness direction of the clutch weight 120.
  • the spring support 115 is formed on the side plate 114 side opposite to the swing support pin 113.
  • the torsion spring 116 has a distal end 121a portion of one of the two clutch weights 120 in which both ends 116b and 116c are located on both sides of the swing support pin 113 in a state where the coil portion 116a is fitted to the spring support 115. And the other neighboring end 121b.
  • the swing support pin 113 serving as a swing support point of the clutch weight 120 is disposed on the outer edge of the drive plate 110 at a position adjacent to the far end 121a of the clutch weight 120. Since the torsion spring 116 is supported, the components constituting the centrifugal clutch 100 can be densified to reduce the device configuration. Further, since the centrifugal clutch 100 is provided with the torsion spring 116 on the opposite side of the clutch weight 120 from the drive plate 110, compared to the case where the torsion spring 116 is disposed between the drive plate 110 and the clutch weight 120. The assembly work of the torsion spring 116 can be facilitated, and the manufacturing burden and the maintenance burden can be reduced. In FIG.
  • the centrifugal clutch 200 can also arrange the torsion spring 116 between the drive plate 110 and the clutch weight 120 as described above.
  • the centrifugal clutch 300 forms the spring support 115 in the clutch weight 120 on the drive plate 110 side, as shown in FIG.
  • the two end portions 116b and 116b of the torsion spring 116 may be installed between the two clutch weights 120 facing each other as described above, but one end portion 116b is hung on the far end 121a of the clutch weight 120.
  • the other end 116 c can be hung on a through hole formed in the base 111 of the drive plate 110.
  • the clutch outer 130 is omitted.
  • the centrifugal clutch 300 configured as described above, since the end portion 116c of the torsion spring 116 is hooked on the drive plate 110, the wear between the end portion 116c due to the rotation of the clutch weight 120 and the adjacent end 121b of the clutch weight 120.
  • the torsion spring 116 can be miniaturized and the entire apparatus configuration can be miniaturized.
  • the transmission 91 mainly includes a drive pulley 92, a V belt 93, and a driven pulley 94.
  • the drive pulley 92 is a component that is provided on a crankshaft 90 extending from the engine and is directly driven to rotate by the rotational driving force of the engine, and mainly includes a fixed drive plate 92a and a movable drive plate 92b. Has been.
  • the drive pulley 92 is configured such that the movable drive plate 92b approaches or separates from the fixed drive plate 92a by the centrifugal force generated by the rotational drive of the crankshaft 90.
  • a V-belt 93 connected with a driven pulley 94 is hung between the fixed drive plate 92a and the movable drive plate 92b.
  • the V-belt 93 is a component for transmitting the rotational driving force of the drive pulley 92 to the driven pulley 94, and is formed in an endless ring shape in which the core wire is covered with a resin material.
  • the driven pulley 94 is a mechanical device that is rotationally driven by the rotational driving force from the engine transmitted through the drive pulley 92 and the V-belt 93, respectively, and mainly includes a fixed driven plate 94a and a movable driven plate 94b.
  • the fixed driven plate 94a is integrally coupled to the drive plate 110 in the centrifugal clutch 100 via a cylindrical driven sleeve 95.
  • the driven sleeve 95 is attached to the drive shaft 101 connected to the rear wheel of the motorcycle via a bearing so as to be relatively rotatable.
  • the driven shaft 95 is engaged with a drive plate 110 so as to be able to rotate integrally with a drive shaft 110 formed at a central portion of the base 111 of the drive plate 110.
  • the movable driven plate 94b is fitted on the driven sleeve 95 while being slidable in the axial direction while pressing the drive plate 110 via the torque spring 96.
  • the driven pulley 94 is configured such that the movable driven plate 94b approaches or separates from the fixed driven plate 94a by the tensile force of the V-belt 93.
  • the transmission 91 has a diameter sandwiching the V belt 93 defined by the distance between the fixed drive plate 92a and the movable drive plate 92b, and a V belt defined by the distance between the fixed driven plate 94a and the movable driven plate 94b.
  • the engine speed is changed in a stepless manner depending on the magnitude relationship with the diameter across 93.
  • the centrifugal clutches 100, 200, and 300 are configured as a so-called leading type in which the far end 121 a side of the clutch weight 120 is the front in the rotational direction of the drive plate 110.
  • the centrifugal clutches 100, 200, and 300 may be configured as a so-called trading type in which the vicinity end 121 b side of the clutch weight 120 is the front in the rotational direction of the drive plate 110.
  • the centrifugal clutches 100, 200, and 300 are used with the torsion spring 116 being rewound from the clutch weight 120.
  • the torsion spring 116 is formed so that the inner peripheral portion of the coil portion 116 a contacts the outer peripheral portion of the spring support 115 in a state where the clutch weight 120 is separated from the clutch outer 130. The backlash can be suppressed.
  • the torsion spring 116 can also be used in a state of being wound around the clutch weight 120. That is, the torsion spring 116 can be used by closing both end portions 116b and 116b of the torsion spring 116 in the direction in which the winding of the coil portion 116a is narrowed and hooking the clutch weight 120.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
PCT/JP2017/028742 2016-10-06 2017-08-08 遠心クラッチ WO2018066223A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201780057181.3A CN109844345B (zh) 2016-10-06 2017-08-08 离心离合器
EP17858063.5A EP3524842A4 (en) 2016-10-06 2017-08-08 CENTRIFUGAL CLUTCH
US16/339,660 US11060569B2 (en) 2016-10-06 2017-08-08 Centrifugal clutch

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-198247 2016-10-06
JP2016198247A JP6811986B2 (ja) 2016-10-06 2016-10-06 遠心クラッチ

Publications (1)

Publication Number Publication Date
WO2018066223A1 true WO2018066223A1 (ja) 2018-04-12

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PCT/JP2017/028742 WO2018066223A1 (ja) 2016-10-06 2017-08-08 遠心クラッチ

Country Status (5)

Country Link
US (1) US11060569B2 (enrdf_load_stackoverflow)
EP (1) EP3524842A4 (enrdf_load_stackoverflow)
JP (1) JP6811986B2 (enrdf_load_stackoverflow)
CN (1) CN109844345B (enrdf_load_stackoverflow)
WO (1) WO2018066223A1 (enrdf_load_stackoverflow)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
EP3795852A4 (en) * 2018-05-18 2022-01-19 Kabushiki Kaisha F.C.C. CENTRIFUGAL CLUTCH

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11096328B2 (en) * 2018-12-27 2021-08-24 Cnh Industrial America Llc Agricultural header with damage-reducing clutch
CN112709784B (zh) * 2020-12-23 2021-10-15 中国人民解放军国防科技大学 一种转动惯量连续可变的自适应展开式飞轮
CN117128257A (zh) * 2022-05-18 2023-11-28 米沃奇电动工具公司 离合器机构

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CN109844345A (zh) 2019-06-04
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